Sole splitting machine



Oct. 3, 1961 F. B. SWEENEY SOLE SPLITTING MACHINE INVENTOR.

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I MOM INVENTOR. FRANK. B. SWEENEY Oct. 3, 1961 F. B. SWEENEY 3,002,207

SOLE SPLITTING MACHINE Filed Aug. 13, 1958 6 Sheets-Sheet 3 INVENTOR.

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Oct. 3, 1961 F. B. SWEENEY SOLE SPLITTING MACHINE 6 Sheets-Sheet 4 Filed Aug. 13, 1958 INVENTOR.

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FRANK B. SWEENEY Oct. 3, 1961 F. B. SWEENEY 3,0

SOLE SPLITTING MACHINE Filed Aug. 15, 1958 6 Sheets-Sheet e FIG. 6

H I IIIIIIII/ll/I/l a? llllllll l INVENTOR. FRANKB. SWEENEY 3,002,207 SOLE SPHTTENG MACHINE Frank B. Sweeney, Rochester, N.Y., assignor to Endicott Johnson Corporation, Endicott, N.Y., a corporation of New York Filed Aug. 13, 1958, Ser. No. 754,801 '7 flaims. (Cl. 12-17) In general, this invention relates to a structurally and functionally improved article thickness reducing machine and more specifically to an improved machine for splitring soles and the like.

An object of this invention is to provide an improved machine for splitting soles so that two or more soles are possible from a single prefabricated article having a sole configuration, and in cases where this article is molded and formed with integrally extending flashes, to increase the number of soles from an article to be trimmed of its flash.

Another object is to provide an improved machine for splitting soles formed from such material as rubber or leather, and if desired a machine for reducing the thickness of these soles during a sole trimming operation.

Still another object is the provision of readily replaceable power feed rolls after they have served their usefulness in apparatus for splitting soles and the like.

A further object is the provision of a power driven roll assembly for a sole splitting machine which can be readily adjusted and which possesses that degree of resiliency for enhancing power roll life.

A still further object is the provision of a sole splitting machine having power driven rolls mounted on pivotal arms which cooperate to couple these rolls to a gear train which, in turn, is so constructed and arranged to have certain of its components shift in response to the pivoting of the arms without detrimentally afiecting the gear drive for the power rolls.

An important object is the provision of a sole splitting machine having power driven rolls mounted on pivotal arms which are adapted to be adjusted relative to one another by means of a diiferentially pitched threaded shaft adjusting mechanism which may have coupled therewith a chain and sprocket arrangement for insuring uniform relative shifting of another similar adjusting mechanism.

Another important object is to provide a sole splitting machine capable of optimum output and embracing relatively few parts, each relatively simple and inexpensive to manufacture as well as assembly at decreased costs, and further which machine possesses the element of adjustability and interchangeability as well as versatility in its application to particular articles to be reduced in thickness or split.

Numerous other objects and advantages will become apparent from the following description of the invention, which is to be taken in conjunction with the accompanying drawings illustrating a single practical embodiment, in which:

FIG. 1 is a top plan view of a sole trimming machine constructed in accordance with the present invention, with certain parts broken away and removed and with other parts broken away and sectioned;

FIG. 2 is a side elevational view of this machine with certain parts broken away and removed;

FIG. 3 is a sectional view taken along the line 33 of FIG. 1;

FIG. 4 is an end elevational view with certain parts broken away and sectioned and other parts broken away and removed;

FIG. 5 is another similar end elevational view of this machine with the diiferential gear transmission train E 5% 3,002,207 Patented Oct. 3, 1961 i2 sectioned and with other parts broken away and sectioned;

FIG. 6 is an exploded perspective view of the ditferential gear transmission train and associated structure for driving the feed rolls of this embodiment which, for purposes of this view, are partly broken and removed;

In the drawings, numeral 14 represents a portion of the top of a table support. This table support 10 conveniently mounts a pair of foot rests 12 and 14 which form a part of the frame of the subject sole splitting machine. Additionally included within this framework is a pair of side plates 16 and 18 which are secured in suitably formed notches in the foot rest 12. A pair of auxiliary plates 26) and 22 are secured to the outer face of side plates 1e and 18, respectively, and together with the latter plates, are fixedly mounted in suitably formed notches in the foot rest 14. A plurality of tie rods 24 are interposed between the side plates 16 and 18 and are suitably anchored therein for cooperating in maintaining these plates in the desired spaced-apart relationship. However, it is preferred that these tie rods be appropriately located so that they do not interfere with the various functional elements of the apparatus' Reference is now made to the hopper and feed assembly, designated generally by the numeral 26, for feeding sequentially one of a plurality of stacked articles, which for purposes of this description, will be taken to be molded soles, to the actual splitting or thickness reducing stage. The hopper side walls of this assembly are defined by zones of the side plates 16 and 18, as well as the adjustable gate slide 28 which is slidably mounted on the transversely extending partition plate Shin substantial face-to-face contact. The gate slide 23 has extending laterally therefrom a tapped adjusting nut 32 which is displaceable in a longitudinally extending slot 34 formed in the partitioning plate 359. A mounting block 36 is fixed to the partitioning plate 359 and includes a bore 37 through which passes a threaded adjusting screw 38 having a knurled adjusting screw knob 40. The adjusting screw 38 is ordinarily engaged with the internal threads presented by the adjusting nut 32 and ponsequently, when. the adjusting screw knob 4% is turned in either a clockwise direction or counter-clockwise direction, a corresponding longitudinal displacement will be effected of the slide 23 with respect to the partitioning plate 30.

An endless conveyor belt assembly 41 functions to feed an unsplit sole to the cutting stage of my sole splitting machine and additionally to present the lower or bottom mounting surfaces of the hopper and feed assembly 25 for cooperating to mount a plurality of unsplit soles in a substantially stacked arrangement. Included in this conveyor belt assembly 41 is a roll 42 and belt conveyor 43.

The roll d2. comprises a shaft 44 journaled in suitable bearings 46, which are mounted by the side plates 16 and 18 substantially as illustrated. A pair of roller elements 48 and 56 are mounted on the rotatable shaft 44 to complete this particular roller structure. As will become apparent shortly, this roller cooperates with the trailing edge of the endless belt conveyor 43 as well as the beveled face 52 of the gate slide 28 to maintain the stacked unsplit soles in the hopper and feed assembly 26 at an incline with respect to the horizontal or plane of the upper receiving surfaces of the subject endless belt conveyor 43. These conveyor belt receiving surfaces in conjunction with the lower edge of the gate slide 28 function to permit a single unsplit sole to pass through the gate opening presented thereby. It has been found that the sole immediately above the lowermost sole in the hopper and feed assembly 26 had a tendency t pas b eat t t 2 becau 9 th reasonabl amount of friction present between contacting unsplit soles, especially when they are formed from a moldable rubber composition. Consequently, this amount ofrfriction is minimized by arranging the unspiit soles above the lowermost sole in the hopper and feed assembly :2 6 1 at an incline with respect to the reccivingsurfaces of the endless belt conveyor 43. By providing an ingline of approximately 15, the lowermost unsplit sole, which will assume a horizontal position, is ermitted to pass through the gate slide 23 without hindering or up- --,setting the desired inclination of the remaining unsplit ,so1e

-As. mentioned in the above, the endless belt conveyor jllu'siadapted to feed the lowermost unsplitsole in the {hOPPCI and feed assembly 25 to the splitting stageof my ,sole splitting machine. This belt conveyor 43 includes a plurality of ribbon-type endless belts These endless bolts 54 are mounted on a pulley drive 56 and driven rolls 58 and as. In an effort to prevent undue tlexure -.of the ribbon-type endless belts 541, when supportingan unsplit sole, a pair of supporting rolls s2 and 64 are advantageously employed. Rolls 58, 6t 62 and 64 may in ,most respects be identical and include a shaft 66 journaled in suitable bearings 68, which, except for those of roll all, are mounted by the side plates 16 and 1S. fl'heshafts 65 mount a pair of collars ill and 72 which are formed with suitable recessed portions 73 to accommodate the selected number of ribbon-type endless belts Referring now LO the pulley drive 56, it will be observed that a series or" pulleys 7d are mounted on a shaft 176 which is journaled in suitable bearings '73 mounted ;.by the side plates 16 and 18. An end of the shaft 7d extends through the side plate 16 and mounts a coupling .80 which transmits the drive energy supplied by a pneurnatic circuit. This pneumatic circuit includes the usual air motor 182 which drives a reduction gear assembly 84, which is mounted by a pair of reduction gear assembly blocks 86 and 38, and is suitably connected with the coupling $0. "The pressurized air for motor 32 is supplied from a conventional source for such medium through an inlet jhne 90. A gauge 92 is provided in this inlet line fi for association with an air flow adjusting valve %4 which is similarly inserted in the inlet line as. Amain air'On- Qfi valve 96 is interposed between the adjusting valve 94 and the air motor 32. Thus, when the main valve :36 'is opened to provide access for the pressurized air which energizes the air motor 82, and consequently the reduction gear assembly 84 to ultimately impart rotational movement to the drive pulley 56 through the coupling St the machine operator need only adjust valve 94 to correspond to any particular pre-selected power output for the air motor 82.

As will be evident from the drawings, the trailing edge of the endless belt conveyor 43 is disposed at a location beyond the gate slide 52 as well as the partitioning plate ,30, to thus feed the lowermost unsplit sole in the hopper and feed assembly 26 to the cutting stage'for my sole splitting machine. As the unsplit soles pass beneath 'the gate slide 28, they encounter a pair of power driven rolls 1% and 192 and are fed thereby into the cutting blade 104 and thus split into two sections. Suffice it to say at this time, these power rolls 1% and 11B? are driven "by means of a transmission gear train 106 which is advantageously coupled with a suitable power source. The upper power roll 1% is supported by a pair of upper arms 108 and 110 which are interconnected by a tie block 111. These arms 1% and 11 are swivelly mounted on a spacer rod 112 by means of bearings 114. This rod 112 mounts a collar 116 which is interposed between the side plates 16 and 18 and functions as aspacer for 1 these plates. A series of thrust washers 118 are suitably -.-positioned upon the spacer rod 112 adjacent its aforementioned mounted components substantially as illustrated. A collar 120 is provided on the end of'the rod 112 adjacent the side plate 16 for preventing lateral displacement of this rod 112 in a direction towards the right as viewed in FIG. 5. In this figure it will be appreciated that the other end-of this rod 112 is extended to provide a mounting for a part of the transmission gear train 166.

The other power driven roll 102 is similarly supported by lower'arrns 122 and 1254 which in turn are swivelly mounted on a spacer rod 126 by means of suitable bearings 128. A collar 130 is mounted on the spacer red 1 26 and cooperates inmaintaining the side plates 16 and 18 in th'e desiiied spaced-apart relation. A plurality of thrust washers 132 are again advantageously employed as shown. Collar 134 prevents lateral d splacement of the spacer rod 126 in a direction toward theright as viewed in FIG. 5.

This spacer rod126 includes a central bore 136 shown in phantom foraccomrnodating grease introduced through a grease fitting 138 located adjacent the collar ass.

It should benoted at this point that the shaft 66 for the roller 60 of the belt conveyor 43 is journaled in .the lower arms 1.22 and 124,. Consequently, the trailing edge of the belt conveyor 43 is shiitable with the lower power roll 102 upon any swivel action of the lower arms 122 and 124 about rod 126. Thus, a suitable disposition of the conveyor trailing edge and lower power roll is assured notwithstanding their permissible displacement.

The upper arms 1G8 and 113, on the other hand, pivotally mount-a pair of idler lever arms 146 and 1 42, respectively. A shaft 144 is journaled in the free end of these idler leverarms with suitable bearings provided therein. A pair of washers 146 as well as a pair of col lars 148 and 150 are mounted on the idler shaft 144. Thus it will be apparent that an idler roll is provided which will function to engage an unsplit sole as it approaches the trailingedge of the conveyor belt assembly 43 before passing through the power drive rolls liltland 102.

Referring now to the knife 104, it will be observed thata single beveled face 151 is provided which is cooperable "wltha lower fiat face 152 in determining the cutting edge 154. Thus it will be apparent that regardless of any elfects of cutting operations or sharpening applications, the cutting edge 154 will be disposed in a plane determined by the lower face 152 of the knife 104. The knifeassembly further includes a knife holder 156 which rests suitably upon formed surfaces of side plates 16 and 18 as well as auxiliary plates 2t? and 22. The

knife blade 104 is adjustably mounted on a plate 158 secured to the knife holder 156. Plate 158 includes a bevelededge 160 cooperable to deflect the lower portion of a split sole in a downward direction and thus follow a selected path. A knife backer 162 is secured to plate 153 and mounts a pair of threaded bolts 164, which, in turn, engage the threads of tapped bores 166 located in theknife blade 1%. When the bolts 16% are rotated about their longitudinal axis, the blade 104 will accordingly shift in a substantially horizontal plane to place the cutting edge 154 to its most advantageous position and orientation. To prevent the blade 1114 from being undesirablyv disassociated with the plate 158, a pair of locking screws 168 are supplied for anchoring the blade 1% to the plate 158 after the correct adjustment has been obtained by means of the adjusting screws 164.

The upper arms 168 and 118 securely mount an upper arm extension- 17h and 172, respectively. These extensions 170 and 1721 are respectively provided [with bores 174 and 176, which are preferably aligned with their associated bores 178 and .181 formed in knife holder 156.

The lower arms 122 and 124 similarlymount extensions 182 and 184, respectively. Bores 186 and 188 are 'tially coaxial with associated bores 17S and 184 in knife holder 156.

An elongated screw 1% is adapted to freely pass through the bores 174, 178 and 186. The upper end of the screw 190 includes an adjusting knob 192, while the lower end thereof threadedly engages a tapped nut 194. The nut 194 is adapted to transfer stresses to and from the lower face of the lower arm extension 182 through a washer 196. The adjusting knob 192 is provided with a boss extension 198 having an annular flange 2% as well as sprockets 202 for meshing with a chain 204. The annular flange 2% supports one end of a spacer plate 225. A spring adjusting nut 206 is positioned adjacent the boss 198 and similarly includes sprockets 298 for a second chain 219. A spring 212 surrounds a portion of the shaft 190 and'is biased at one end against lower faces of the screw adjusting nut 2% and at the other end with a bearing washer 214. Obviously, when the nut 2% is rotated relative to the shaft 190, the bias of the spring 212 will be correspondingly changed.

Another adjusting nut 216 is placed on the shaft 190 for adjusting the bias of spring 218. As illustrated, one end of the spring 218 is compressed against the adjusting nut 216 with the other end bearing against a washer 219, which rests upon the knife holder 156. A projection 221i extends upwardly from nut 214 for engagement with a key slot 221 in the lower face of arm extension 176. A further adjusting nut 222 is positioned on the screw 19!) and disposed below the lower face of the knife holder 156. A projection 224 extends from the upper face of nut 222 and is associated with a detent 226 formed in the lower face of the knife holder 156 adjacent the bore 178.

' A similar arrangement of parts are provided on the extensions 172 and 184. In this connection, a screw 239 extends through bores 176, 180 and 128 and includes an adjusting knob 232 from which extends a boss 234 having an annular fiange 236 and sprockets 238 for engaging the chain 2il'4. The fian e 231 provides the necessary support for the other end of spacer plate 2%.

A nut 24%, through washer 242, provides a support for the lower arm extension 184. An adjusting nut 244 is mounted on the screw 230 adjacent the boss 234 and includes sprockets 246 which cooperate with the chain 210. A spring 2 23 encircles screw 23% and is biased against the lower face of the adjusting nut 244 and upper face of a washer 25% which bears against the upper face of the upper arm extension 172. An adjusting nut 252 is located on the screw 23ft beneath the lower face of the upper arm extension 172 and cooperates with a washer 254 which rests upon the knife holder E56 for suitably compressing a spring 255. A projection 256 projects from the nut 252 and suitably engages with a slot 257 in the upper arm extension 172. An adjusting nut 253 is in engagement with the screw 23% and is provided with a projection 264 which is adapted to be disposed within the detent 262 in the knife holder 156 adjacent bore 18%.

Thus, when the screws 1% and 230 are similarly rotated, the power driven rolls 165i and 192 will shift relative to one another as well as with respect to the cutting edge 154 of blade 1%. in this connection, it should be apparent that chain 2ft enables adjusting nuts 2'36 and 244 to act in unison and thus relieve or increase the bias of springs 212 and 243, respectively, either with th rotation of screws 1% and 23 or upon the rotation of the subject adjusting nuts. Since adjusting nuts 2 6, 222, 252 and 25% are keyed and thusly not rotatable with their associated screw, they will be displaced longitudinally relative to such screw upon rotation of either screw. Consequently, the rolls tilt! and 102 will shift when either screw is rotated. When these power driven rolls liill and 102 are rotating to feed an unsplit sole into the blade 104, they should firmly engage thisunsplit sole so that the latter does not undesirably shift during the splitting stage.

Accordingly, the screws 190 and 230 should be turned so that their associated springs wll provide the necessary resiliency to insure this firm contact. Of course, the bias of the screw mounted springs are properly established by means of their associated adjusting nuts.

To insure that the axis of the power driven rolls and 104 are maintained in their desired parallel relationship upon the turning of the screws and 23f), the interconnecting chains 204 and 210 will reduce to a negligible amount the permissible rotation of one screw relative to the other. In effect, the rotation of each screw will be substantially identical by means of this chain-and sprocket structure. Thus, by simply grasping and turning either knob 122 or 232, to effect rotation of the corresponding screw, the other screw will be actuated and turned substantially instantaneously and equally.

Obviously, when the upper drive roll 1530 is displaced, a unit distance with respect to the cutting edge 154 of blade 1G4, the other power roll 102 should be similarly displaced in the other direction to cooperate to split a sole into two equal parts. Therefore, the mere rotation of the screws 1% and 23s should effect this relative displacement. Thus, the pitch of the threads presented by these screws can be modified along their respective lengths to accommodate this desired displacement. In this connection, the pitch of the threads above the upper face of the knife holder 156 should be in the ratio of 1:2, in comparison with the pitch of the threads below this face.

A bracket 270 projects laterally from the auxiliary plate 22 and includes an upstanding plate 272 which is adapted to support the cantilevered ends of shafts 122 and 126 as well as their associated gears. As shown, the cantilevered end of upper shaft 112 is provided with an internal bore 2'74 and laterally extending passages for a suitable lubricant which is inserted through a grease fitting 276. A retaining collar 278 is adjacent the grease fitting 2-76 and is adapted to maintain gears, which are to be described shortly, on the shaft 112.

Initially, a differential bevel gear 286 is keyed to shaft 112 adjacent collar 278 by means of the usual key structure 282. A differential spider 234 is next positioned on the shaft 112 by means of a suitable bearing 286. A

second differential bevel gear 288 is mounted on shaft 132 through bearing 2% and has portions thereof extending through upstanding plate 272 and is associated therewith by means of a bearing 292. At least three bevel pinions 2% are engaged with the bevel gears 28% and 28S and extend radially from the axes of the shaft 112 by means of mounting studs 296 and bushings 297. A V- belt pulley 298 is mounted on the spider 284, with bearings 300 interposed between the pinions 2% and the V- belt pulley 298. As will be appreciated by those skilled in the art, the V-belt pulley 298 is adapted to be connected to the usual power source for transmitting rotational energy to the shaft 112.

A bushing 3G2 ensleeves shaft 112 adjacent bearing 2%, with portions of the bevel gear 288 surrounding a part of its outer face. It should be understood at this time that the gears which are mounted on bushings in the gear train are fixedly secured thereto. A gear 3&4 isthen positioned over the remaining portion of the outer face of bushing 302. Bushing 306 is similarly mounted on the shaft 112 and spaced from bushing 322 by means of a thrust washer 308. A gear 310 is mounted on this bushing 306 and is spaced from a similarly mounted gear 312 by means of a thrust washer 314. A gear 316 is keyed to shaft 112 at 318 and is spaced from the bush-- ing 3% as well as gear 312 by means of a thrust washer- 322. A third bushing 322 is mounted on the shaft 112: with the thrust washer 324 separating it from the gear 316. A gear 326 embraces part of the outer face of this. bushing 322 and is separated from a gear 328 which surrounds at major portion of the remaining part of the outer face of this bushing by means of a thrust washer 330. The gear 328 and its associated part of bushing 322 are spacedfrom thearm-lltl as well as bearing 114 by means of ,an aforementioned thrust washer 24.18.

Referring now to the shaft res, it will be observed that its end, distal the grease fitting 13b, is associated with and supported by the upstanding plate 272 by means of a bearing 332. A retaining ring 334 functions to prevent any undesirable longitudinal shifting of the shaft 126. A bushing 336 embraces the shaft 126 and mounts gears 333 and 3 40 which are separated from one another by means of a thrust washer 342. The teeth of gear are engaged with the teeth of gear SW- of upper 112, while teeth of gear 348 engage teeth of gear 31% of this shaft. A gear 344 is keyed to the shaft 12s at 346 and is spaced from the bushing 336 and gear 348 by a thrust washer 548. This gear meshes with the gear 31?, which is mounted on the upper shaft HZ. A second bushing 350 is located on the shaft 126 and is spaced from the gear 344. by means of thrust washer 352. Gears and 356, together with an interposed washer are mounted on the bushing 350, with gear 354- engaging gear and gear 356 engaging gear 326. A gear 36d is keyed to shaft 12s by a key structure 362 and is spaced from the gear 356 as well as bushing 350 by means of a thrust washer 364 and from lower arm 124 by means of a thrust washer 332.

A gear 365 is keyed to an upper power roll ran as at 3 66 and is rotatable upon rotation of the gear 328 by means of the interposed gear 3-67. Gear 367 is rotatably mounted on a stud 363, which is threadedly engaged with surfaces of the upper arm 119, by means of bearing 369.

The lower power driven roll 102 similarly has a gear 374) keyed thereto and which is meshed with gear 3? which, in turn, engages gear 364 Gear 3'72 is mounted on a stud 374- on the lower arm 124 by means of bearing 376. Thus, the lower power roll 1% will rotate upon rotation of the gear 366. It should be noted that irrespective of any displacement of the power rolls ltd and 102, the desired spaced-apart and parallel relationship of the axes of the gears 365, 367 and 523, on one hand, and gears 37%, 372 and 36d, on the other hand, will be maintained with the mating gear teeth in proper engagement.

In FIG. these are illustrated as paths of force created when the power rolls llitl and W2 are rotated. It is preferable that these rolls rotate at substantially the same surface speed in feeding an unsplit sole into the knife 104. However, in practice it has been found that from time to time the surface speeds of the power rolls Hill and 192 will not be identical for a plurality of reasons. When this is encountered, the gear train 1%, because of its specific design, will compensate for the differential in power roll surface speeds and function to restore them to equality as Well as to maintain these speeds at their propor values. In this connection, torques will be established in the gear train res when the power roll surface speeds are not equal. These torques will be eliminated by the permissible relative rotation of the bevel gear 238 and 280. This relative rotation is accomplished through the interposed pinions 294 between bevel gears 28! and 288.

Although the sole splitting machine is adapted to minimize undesirable wear of the power rolls lllft an 162, it is contemplated that in time these rolls will be detrimentally elfected by extensive use. Therefore, provisions are made for structure by which these rolls can be replaced without affecting other components of my machine within a minimum amount of time without encountering pronounced difficulty.

Accordingly, the upper power roll 1% may include a knurled sleeve 3% on an axle 332., one end of which is journaled in the arm ltlfi by means of bearing 384. The other end of the aide $82 is coupled with a sleeve 386 journaled in arm 11% by means of bearing 383 and advantageously mounts the gear 36G through the key structure 362'. A key 389 interconnects sleeves 33b and 386 to enable both of these sleeves to rotate together. A colv r "v lar .390 is mounted on a threaded extension of the sleeve 336 and cooperates to maintain the gear 36% on the sleeve 386. A thrust washer 392 may be interposed to maintain the desired spaced-apart relationship between arm llltl and gear 366.

Since the lower power roll 192 includes substantially the same structure as the aforedescribed power roll 190, a detailed description of the structure involved in the former will not be resorted to at this time.

Thus, it should be apparent that this invention contemplates a mechanism for insuring the proper feeding .of an unsplit sole into the blade 104. Additionally, the disclosed machine can split into equal segments a sole fabricated from either leather, rubber or other materials employed for this purpose. If desired, this machine can be utilized to simply reduce the thickness of a particular sole. Power roll life is obviously increased by this machine; and the incorporated power rolls are peculiarly adapted to more eifectively split or merely reduce in thickness soles and similar articles by means of their drive means as well as their supporting means. In this connection, these power rolls are independent of their driving shafts and, therefore, are capable of being replaced without complete removal of the drive shaft when the feed roll collars wear beyond the permissible limit. it has been found that the aforedescribed machine significantly increases the output of a single operator in comparison with existing and known sole splitting machines to such an extent as to practically double the operator output.

Thus, among others, the numerous objects and advantages are most effectively attained. Although a single practical machine has been described and illustrated, it will be understood that this invention is to be defined by the scope of the appended claims.

I claim:

1. in a thickness reducing machine for soles and the like, including a member having a cutting edge cooperable to reduce one of a plurality of stacked articles to be reduced, which machine further includes a power driven means for feeding said one of said articles to said member such that said one of said articles is reduced by said cutting edge, said power driven means including a differential transmission gear train and two rollers driven by said train for presenting automatically adjustable surface speeds upon engagement of said one of said articles.

2. In a thickness reducing machine for soles and the like, including a member having a cutting edge cooperable to reduce one of a plurality of stacked articles to be reduced, which machine further includes a power driven means for feeding said one of said articles to said member such that said one of said articles is reduced by said cut. ting edge, said power driven means including a pair of power rolls, a differential gear transmission train for driving said rolls, said gear train cooperable to difierentiate between the surface speeds of said rolls and subsequently cooperate to adjust the surface speed of said one of these rolls to correspond with the speed of the other roll.

3. A thickness reducing machine for soles and the like comprising in combination: a hopper and feed assembly for supplying one of a plurality of stacked articles to be reduced, said assembly including a driven conveyor belt mechanism having a trailing edge; a member having a cutting edge cooperable to reduce said one of said articles and power driven means including at least one power driven roll for feeding said one of said articles supplied by said hopper and feed assembly to said member such that said one of said articles is reduced by said cutting edge, a pair of pivotal arms rotatably mounting said roll, and means engageable with surfaces of said arms for varying the disposition of said roll with respect to said cutting edge, said trailing edge of said conveyor belt mechanism being additionally rotatably mounted by said pivotal arms and thus being shiftable upon the varying of the disposition of said roll with respect to said cutting edge.

4. In a thickness reducing machine for soles and the like, including a member having a cutting edge cooperable to reduce one of a plurality of stacked articles to be reduced, said machine further including power driven means for feeding said one of said articles to said member such that said one of said articles is reduced by said cutting edge, said power driven means including a pair of power rolls, shiftable means for mounting each of said rolls, and adjusting means engageable with said shiftable means for varying the disposition of said rolls with respect to said cutting edge, said adjusting means being so constructed and arranged to adjust one roll a unit amount with respect to said cutting edge in one direction while simultaneously therewith adjusting the disposition of the other roll with respect to said cutting edge by an amount substantially equal to that of said unit amount in the other direction.

5. The invention in accordance with claim 4, wherein two similar adjusting means are engageable with said shiftable means, and means interconnecting said two similar adjusting means such that upon actuation of one of said adjusting means, the other adjusting means will be simultaneously and identically actuated.

6. A thickness reducing machine for soles and the like comprising in combination: a hopper and feed assembly for supplying one of a plurality of stacked articles to be reduced; a member having a cutting edge cooperable to 10 reduce said one of said articles; and power driven means for feeding said one of said articles supplied by said hopper and feed assembly to said member such that said one of said articles is reduced by said cutting edge, and said power driven means including a differential transmission gear train and two rollers driven by said train for presenting automatically adjustable surface speed upon engagement of said one of said articles.

7. A thickness reducing machine for soles and the like comprising in combination: a hopper and feed assembly for supplying one of a plurality of stacked articles to be reduced; a member having a cutting edge cooperable to reduce said one of said articles; and power driven means for feeding said one of said articles supplied by said hopper and feed assembly to said member such that said one of said articles is reduced by said cutting edge, said power driven means including a pair of power rolls and a differential gear transmission train for driving said rolls, and said gear train being cooperable to ditferentiate between the surface speeds of said rolls and subsequently cooperate to adjust the surface speed of one of these rolls to correspond with the speed of the other roll.

References Cited in the file of this patent UNITED STATES PATENTS 

